CN218934727U - Compression mechanism, rotary compressor and refrigeration cycle device - Google Patents
Compression mechanism, rotary compressor and refrigeration cycle device Download PDFInfo
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- CN218934727U CN218934727U CN202223265849.0U CN202223265849U CN218934727U CN 218934727 U CN218934727 U CN 218934727U CN 202223265849 U CN202223265849 U CN 202223265849U CN 218934727 U CN218934727 U CN 218934727U
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Abstract
The utility model discloses a compression mechanism, a rotary compressor and a refrigeration cycle device, wherein the compression mechanism is used for the rotary compressor, and the compression mechanism comprises: a crankshaft including an eccentric shaft; the cylinder is provided with a compression cavity and a sliding vane groove communicated with the compression cavity; the piston is sleeved on the eccentric shaft and can eccentrically rotate in the compression cavity; the sliding vane can be arranged in the sliding vane groove in a reciprocating sliding manner, and the head part of the sliding vane is propped against the outer diameter surface of the piston; the inner diameter of the cylinder is D, the outer diameter of the piston is R, the eccentric amount of the eccentric shaft is e, the thickness of the sliding vane is T, and the head radius of the sliding vane is Rv; at least one of the following relationships is satisfied: t is more than or equal to 0.16, and Rv/R is less than or equal to 0.31; T.ltoreq.e/D.ltoreq.0.29. The technical scheme of the utility model can improve the efficiency and reliability of the rotary compressor.
Description
Technical Field
The present utility model relates to the field of compressors, and more particularly, to a compression mechanism, a rotary compressor, and a refrigeration cycle apparatus.
Background
The rotary compressor is to directly drive the piston to eccentrically rotate in the cylinder by the motor to compress the refrigerant. The rotary compressor has less parts and simple structure; few vulnerable parts, reliable operation and the like. Such compressors are more suitable for small refrigeration cycle devices, such as small air conditioners, and are more widely used, particularly in domestic air conditioners.
Energy saving and environmental protection are two main subjects of refrigeration and air conditioning industries. In view of the gradual increase of the current energy-saving requirements, the energy efficiency grade requirements of the air conditioner are further increased. On the premise of ensuring reliability, in order to improve the efficiency of the compressor, each working component of the compressor needs to be optimized, and the size is set in an optimal interval so as to achieve the optimization of the efficiency of the compressor.
Disclosure of Invention
The utility model mainly aims to provide a compression mechanism, which aims to improve the energy efficiency and the reliability of a rotary compressor.
In order to achieve the above object, the present utility model provides a compression mechanism for a rotary compressor, the compression mechanism comprising:
a crankshaft including an eccentric shaft;
the cylinder is provided with a compression cavity and a sliding vane groove communicated with the compression cavity;
the piston is sleeved on the eccentric shaft and can eccentrically rotate in the compression cavity; and
the sliding vane is arranged in the sliding vane groove in a reciprocating sliding manner, and the head part of the sliding vane is propped against the outer diameter surface of the piston;
the inner diameter of the cylinder is D, the outer diameter of the piston is R, the eccentric amount of the eccentric shaft is e, the thickness of the sliding vane is T, and the head radius of the sliding vane is Rv; at least one of the following relationships is satisfied:
0.16≤T*Rv/R≤0.31；
0.17≤T*e/D≤0.29。
in one embodiment, the cylinder has an inner diameter D that satisfies: d is more than or equal to 26mm and less than or equal to 44mm.
In one embodiment, the height H of the cylinder satisfies: h is less than or equal to 22mm.
In one embodiment, the thickness T of the slider satisfies: t is less than or equal to 3.1mm.
In one embodiment, the length L of the slider satisfies: 2e/L is less than or equal to 0.4.
In one embodiment, the head of the sliding sheet is provided with a hard film; or the whole surface of the sliding sheet is provided with a hard film.
In one embodiment, the displacement of an individual one of the cylinders is less than or equal to 12cc.
In one embodiment, the compression mechanism further comprises a main bearing and an auxiliary bearing which are respectively arranged at two axial ends of the cylinder, the crankshaft further comprises a main shaft sleeved with the main bearing and a auxiliary shaft sleeved with the auxiliary bearing, the cylinder is provided with an exhaust notch, and the main bearing and/or the auxiliary bearing are/is provided with an exhaust port communicated with the exhaust notch.
The utility model also provides a rotary compressor comprising the compression mechanism.
The utility model also provides a refrigeration cycle device comprising the rotary compressor.
According to the technical scheme, the related parameters of the cylinder, the piston and the sliding vane of the compression mechanism are optimally designed, so that at least one of the following relational expressions is satisfied: t is more than or equal to 0.16, and Rv/R is less than or equal to 0.31; t is more than or equal to 0.17 and less than or equal to 0.29; the sliding vane can be matched with the cylinder and the piston, so that the thickness of the sliding vane is not too thick, the volumetric efficiency of the compression mechanism can be effectively improved, and meanwhile, the thickness of the sliding vane is not too thin, so that the reduction of the volumetric efficiency caused by leakage of the axial end face of the sliding vane is prevented, the rigidity of the sliding vane can be ensured, and the sliding vane has stronger bending resistance and wear resistance. According to the technical scheme, through reasonably designing the matching sizes of the sliding vane, the air cylinder and the piston, the friction power consumption of the compression mechanism can be effectively improved, the volumetric efficiency is improved, the abrasion of the sliding vane is reduced, and the operation reliability of the rotary compressor can be further improved when the energy efficiency of the rotary compressor is improved.
Drawings
In order to more clearly illustrate the embodiments of the present utility model or the technical solutions in the prior art, the drawings that are required in the embodiments or the description of the prior art will be briefly described, and it is obvious that the drawings in the following description are only some embodiments of the present utility model, and other drawings may be obtained according to the structures shown in these drawings without inventive effort for a person skilled in the art.
FIG. 1 is a schematic cross-sectional view of a rotary compressor according to an embodiment of the present utility model;
FIG. 2 is a schematic cross-sectional view of an embodiment of a compression mechanism according to the present utility model;
FIG. 3 is a schematic cross-sectional view of the compression mechanism of FIG. 2;
FIG. 4 is a graph showing the relationship between the product of the thickness of the slide and the head radius of the slide and the ratio of the outer diameter of the piston to the COP value of the compressor;
FIG. 5 is a graph showing the relationship between the product of the thickness of the slide and the eccentric amount of the eccentric shaft and the ratio of the inner diameter of the cylinder to the COP value of the compressor.
Reference numerals illustrate:
| reference numerals | Name of the name | Reference numerals | Name of the |
| 10 | |
13 | Piston |
| 11 | |
14 | Sliding |
| 111 | |
15 | Main bearing |
| 112 | |
16 | Auxiliary bearing |
| 113 | |
20 | |
| 12 | |
30 | Shell body |
The achievement of the objects, functional features and advantages of the present utility model will be further described with reference to the accompanying drawings, in conjunction with the embodiments.
Detailed Description
The following description of the embodiments of the present utility model will be made clearly and fully with reference to the accompanying drawings, in which it is evident that the embodiments described are only some, but not all embodiments of the utility model. All other embodiments, which can be made by those skilled in the art based on the embodiments of the utility model without making any inventive effort, are intended to be within the scope of the utility model.
It should be noted that, if a directional indication (such as up, down, left, right, front, and rear … …) is involved in the embodiment of the present utility model, the directional indication is merely used to explain the relative positional relationship, movement condition, etc. between the components in a specific posture, and if the specific posture is changed, the directional indication is correspondingly changed.
In addition, if there is a description of "first", "second", etc. in the embodiments of the present utility model, the description of "first", "second", etc. is for descriptive purposes only and is not to be construed as indicating or implying a relative importance or implicitly indicating the number of technical features indicated. Thus, a feature defining "a first" or "a second" may explicitly or implicitly include at least one such feature. In addition, if "and/or" and/or "are used throughout, the meaning includes three parallel schemes, for example," a and/or B "including a scheme, or B scheme, or a scheme where a and B are satisfied simultaneously. In addition, the technical solutions of the embodiments may be combined with each other, but it is necessary to base that the technical solutions can be realized by those skilled in the art, and when the technical solutions are contradictory or cannot be realized, the combination of the technical solutions should be considered to be absent and not within the scope of protection claimed in the present utility model.
The present utility model proposes a compression mechanism 10.
Referring to fig. 1 to 3, in an embodiment of the present utility model, the compression mechanism 10 is used for a rotary compressor, and the compression mechanism 10 includes a crankshaft 11, a cylinder 12, a piston 13 and a slide vane 14. The crankshaft 11 includes an eccentric shaft 111; the cylinder 12 is provided with a compression cavity and a sliding vane groove communicated with the compression cavity; the piston 13 is sleeved on the eccentric shaft 111 and can eccentrically rotate in the compression cavity; the sliding vane 14 is arranged in the sliding vane groove in a reciprocating sliding manner, and the head part of the sliding vane 14 is propped against the outer diameter surface of the piston 13; wherein the inner diameter of the cylinder 12 is D, the outer diameter of the piston 13 is R, the eccentric amount of the eccentric shaft 111 is e, the thickness of the sliding vane 14 is T, and the head radius of the sliding vane 14 is Rv; at least one of the following relationships is satisfied:
0.16≤T*Rv/R≤0.31；
0.17≤T*e/D≤0.29。
the compression mechanism 10 is used for a rotary compressor, wherein the rotary compressor may be a single cylinder rotary compressor, a double cylinder rotary compressor, or a multi-cylinder rotary compressor, and is not particularly limited herein. As shown in fig. 1, in an embodiment, the rotary compressor includes a housing 30, a driving motor 20 and a compression mechanism 10, where the driving motor 20 and the compression mechanism 10 are both disposed in the housing 30, specifically, the driving motor 20 may include a stator installed in the housing 30 and a rotor coaxially disposed in the stator, and the stator generates a rotating magnetic field after being energized, and drives the rotor to rotate under the rotating magnetic field of the stator. The rotor of the driving motor 20 is in driving connection with the crankshaft 11 of the compression mechanism 10, and the crankshaft 11 is driven to rotate by the rotor.
The compression mechanism 10 comprises a crankshaft 11, cylinders 12, pistons 13 and sliding sheets 14, wherein the number of the cylinders 12 can be one, two or more according to actual needs, and each cylinder 12 is internally provided with the piston 13 and the sliding sheets 14 matched with the piston 13. The following description will be given mainly by taking the single cylinder 12 as an example. The cylinder 12 is of a hollow annular structure, the cylinder 12 is provided with a compression cavity and a sliding vane groove, the sliding vane groove extends to be communicated with the compression cavity along the radial direction of the cylinder 12, the piston 13 is arranged in the compression cavity and sleeved on the periphery of the eccentric shaft 111, the sliding vane 14 is arranged in the sliding vane groove in a reciprocating sliding manner, and one end of the sliding vane groove, which is far away from the compression cavity, can be provided with an elastic piece elastically abutted with the tail part of the sliding vane 14, so that the head part of the sliding vane 14 is always abutted with the outer diameter surface of the piston 13. In order to ensure that the head of the slide 14 is in good contact with the outer diameter surface of the piston 13, the head of the slide 14 may be provided with an arcuate surface. The piston 13 is driven to eccentrically rotate in the compression cavity of the cylinder 12 by the eccentric shaft 111 of the crankshaft 11, the sliding vane 14 slides in a reciprocating straight line in the sliding vane groove, the compression cavity can be divided into a low pressure side and a high pressure side by the sliding vane 14, a low pressure refrigerant can be sucked into the low pressure side of the compression cavity from the air suction port of the cylinder 12 and changed into a high pressure refrigerant after compression, and then discharged through the air outlet after flowing into the high pressure side, so that the suction, compression and discharge of the refrigerant are realized.
The inventors found that, when designing the compression mechanism 10, if the thickness of the slide sheet 14 is reduced, the suction and exhaust angle can be reduced, and the volumetric efficiency of the compression mechanism 10 can be improved; however, too small thickness of the sliding vane 14 may increase leakage in the axial end face direction of the sliding vane 14, resulting in reduced volumetric efficiency, and too small thickness of the sliding vane 14 may also result in reduced rigidity of the sliding vane 14, and reduced bending resistance, so that the thickness of the sliding vane 14 needs to be reasonably set in combination with relevant parameters of the cylinder 12 and the piston 13, so as to optimize the efficiency of the compressor.
The inner diameter of the cylinder 12 is D, the outer diameter of the piston 13 is R, the eccentric amount of the eccentric shaft 111 is e, the thickness of the sliding vane 14 is T, and the head radius of the sliding vane 14 is Rv; when at least one of the following relationships is satisfied: t is more than or equal to 0.16, and Rv/R is less than or equal to 0.31; T/D is less than or equal to 0.17 and less than or equal to 0.29, so that the volumetric efficiency of the compressor can be improved, the abrasion is reduced, and the efficiency and the reliability of the compressor are improved.
The parameter T Rv/R is the ratio of the product of the thickness of the slide 14 and the radius of the head of the slide 14 to the outer diameter of the piston 13. If the parameter T is excessively large, it is understood that, in the case where the outer diameter R of the piston 13 is unchanged, the thickness T of the vane 14 or the head radius Rv of the vane 14 is relatively large, and if T is excessively large, the thickness of the vane is excessively large, which may cause an excessively large suction and exhaust angle and a reduced volume ratio; if Rv is too large, the closer the head of the slide 14 is to the plane, and when the piston 13 rotates to the left and right extreme positions, the corners of the head of the slide 14 tend to catch the outer diameter surface of the piston 13, causing mechanical wear and affecting performance stability. If the parameter T is too small, it is understood that, in the case where the outer diameter R of the piston 13 is unchanged, the thickness T of the sliding vane 14 or the radius Rv of the head of the sliding vane 14 is relatively small, and if T is too small, the thickness of the sliding vane 14 is too thin, so that the rigidity of the sliding vane 14 is reduced and the bending resistance is reduced; if Rv is too small, the contact area between the head of the vane 14 and the outer diameter surface of the piston 13 is small, which results in an increase in leakage in the axial end face direction of the vane 14 and a decrease in volumetric efficiency. According to the technical scheme, through the optimization design of the thickness and the head radius of the sliding vane 14 and the outer diameter size of the piston 13, when the T is less than or equal to 0.16 and the Rv/R is less than or equal to 0.31, the volumetric efficiency of the compressor can be improved, the abrasion is reduced, and the efficiency and the reliability of the compressor are improved.
Referring to fig. 4, a relationship between the ratio (t×rv/R) of the product of the thickness of the sliding vane 14 and the head radius of the sliding vane 14 to the outer diameter of the piston 13 and the COP value of the compressor is shown in an embodiment. The COP value (Coefficient of performance) of the compressor refers to the ratio of the refrigerating capacity of the refrigerating compressor to the consumed power under a certain working condition, and is called a coefficient of performance. When T is less than or equal to 0.16 and Rv/R is less than or equal to 0.31, the COP value of the compressor is kept in a higher interval range, and the rotary compressor has higher efficiency; when T is more than or equal to 0.16 and Rv/R is less than or equal to 0.31, the thickness and the head radius of the sliding vane 14 are moderate, so that the sliding vane 14 can keep rigidity, and has stronger bending resistance and wear resistance, thereby improving the reliability of the rotary compressor.
The parameter t×e/D is a ratio of a product of the thickness of the vane 14 and the eccentric amount of the crankshaft 11 to the inner diameter of the cylinder 12. If the parameter t×e/D is set too large, it is understood that the thickness T of the vane 14 or the eccentric amount of the eccentric shaft 111 is set relatively large in the case that the inner diameter D of the cylinder 12 is unchanged, and if T is set too large, the thickness of the vane is too thick, which may cause an excessively large suction and exhaust angle and a reduced volume ratio; if e is set too large, the centrifugal force of the slide 14 is increased, and the slide 14 is separated from the contact of the piston 13, thereby affecting the operation reliability. If the parameter t×e/D is set too small, it is understood that the thickness T of the vane 14 or the eccentric amount of the eccentric shaft 111 is set smaller in the case that the inner diameter D of the cylinder 12 is not changed, and if T is set too small, the thickness of the vane 14 is too thin, so that the rigidity of the vane 14 is reduced and the bending resistance is weakened; if e is set too small, eccentric rotation of the piston 13 is not facilitated. According to the technical scheme, through the optimization design of the thickness of the sliding vane 14, the eccentric amount of the eccentric shaft 111 and the inner diameter size of the air cylinder 12, when the T/D is less than or equal to 0.17 and less than or equal to 0.29, the volumetric efficiency of the compressor can be improved, the abrasion is reduced, and the efficiency and the reliability of the compressor are improved.
Referring to fig. 5, a relationship between the product of the thickness of the vane 14 and the eccentric amount of the eccentric shaft 111 and the inner diameter ratio (t×e/D) of the cylinder 12 and the COP value of the compressor is shown in an embodiment. When the value of the COP of the compressor is kept in a higher interval range and the value of the COP of the rotary compressor is not more than 0.17 and not more than 0.29, the rotary compressor has higher efficiency; when T/D is not less than 0.17 and not more than 0.29, the thickness of the sliding vane 14 and the eccentric amount of the eccentric shaft 111 are moderate, so that the sliding vane 14 can keep rigid, has stronger bending resistance and wear resistance, and is beneficial to eccentric rotation of the piston 13 so as to improve the reliability of the rotary compressor.
According to the technical scheme, the related parameters of the cylinder 12, the piston 13 and the sliding vane 14 of the compression mechanism 10 are optimally designed, so that at least one of the following relational expressions is satisfied: t is more than or equal to 0.16, and Rv/R is less than or equal to 0.31; t is more than or equal to 0.17 and less than or equal to 0.29; the sliding vane 14 can be matched with the cylinder 12 and the piston 13, so that the thickness of the sliding vane 14 is not too thick, the volumetric efficiency of the compression mechanism 10 can be effectively improved, and meanwhile, the thickness of the sliding vane 14 is not too thin, so that the reduction of the volumetric efficiency caused by leakage of the axial end face of the sliding vane 14 is prevented, the rigidity of the sliding vane 14 can be ensured, and the sliding vane 14 has stronger bending resistance and wear resistance. According to the technical scheme, through reasonably designing the matching sizes of the sliding vane 14, the air cylinder 12 and the piston 13, the friction power consumption of the compression mechanism 10 can be effectively improved, the volumetric efficiency is improved, the abrasion of the sliding vane 14 is reduced, and the running reliability of the rotary compressor can be further improved while the energy efficiency of the rotary compressor is improved.
To enable a better dimensional matching of the cylinder 12 with the slide 14, in one embodiment, the inner diameter D of the cylinder 12 satisfies: d is more than or equal to 26mm and less than or equal to 44mm. If the size of the inner diameter D of the cylinder 12 is too small, for example, if the inner diameter D of the cylinder 12 is smaller than 26mm, the volume of the compression chamber of the cylinder 12 is small, so that the volumetric efficiency of the compressor is low. If the inner diameter D of the cylinder 12 is too large, for example, if the inner diameter D of the cylinder 12 is greater than 44mm, the slide 14 satisfying the above condition will not be well matched. In the embodiment, through the optimization design of the inner diameter size of the air cylinder 12, the D is more than or equal to 26mm and less than or equal to 44mm, the air cylinder 12 can be well matched with the sliding vane 14 meeting the conditions, the volumetric efficiency of the compressor can be effectively improved, the abrasion is reduced, and the efficiency and the reliability of the compressor are improved. The inner diameter D of the cylinder 12 may be set to 26mm, 30mm, 35mm, 44mm, etc. according to actual needs.
In order to enable a better dimensional matching of the cylinder 12 with the slide 14, in one of the embodiments the height H of said cylinder 12 satisfies: h is less than or equal to 22mm. If the height H of the cylinder 12 is too large, for example, if the height H of the cylinder 12 is greater than 22mm, the height of the slide 14 to be matched is increased accordingly, and this design is disadvantageous in that the slide 14 is thinned, and if the slide 14 is thinned and is high, the rigidity of the slide 14 is lowered. In this embodiment, by optimally designing the height dimension of the cylinder 12 so that H is less than or equal to 22mm, the cylinder 12 can be matched with the slide sheet 14 meeting the above conditions, which is beneficial to the thinning design of the slide sheet 14, and further can effectively improve the volumetric efficiency of the compressor, reduce the wear and improve the efficiency and reliability of the compressor. The height H of the cylinder 12 may be set to 22mm, 20mm, 18mm, 16mm, etc. according to actual needs.
In one embodiment, the thickness T of the slide 14 satisfies: t is less than or equal to 3.1mm. For example, the thickness of the slide 14 may be 3.1mm, 2.9mm, 2.8mm, 2.4mm, etc. Optionally, the thickness T of the slide 14 satisfies: t is less than or equal to 2.8mm. Compared with the sliding vane 14 of 3.2mm commonly used in the current industry, the thickness of the sliding vane 14 of the technical scheme is thinner, so that the suction and exhaust angle can be reduced, and the volumetric efficiency of the compression mechanism 10 is improved.
In order to better bring the slide 14 into abutment with the piston 13, to ensure compression performance, in one of the embodiments, the length L of said slide 14 satisfies: 2e/L is less than or equal to 0.4. For example, the length L of the slide 14 is 21mm, and the eccentricity is 4mm, at which time 2e/L is about 0.38.
To further increase the wear resistance of the slide 14 and increase the reliability of the compression mechanism 10, in one embodiment, the heads of the slide 14 are provided with a hard film; or the whole surface of the slide 14 is provided with a hard film. For example, a hard film may be formed on the head of the sliding vane 14 or the entire surface of the sliding vane 14 by a surface treatment process (such as gas nitriding, gas carbonitriding, etc.), so that the sliding vane 14 contacts with the outer diameter surface of the piston 13 through the hard film, thereby reducing the abrasion of the sliding vane 14 when the piston 13 moves, and improving the service life of the sliding vane 14.
In order to enable the cylinders 12 to better match the vanes 14 meeting the above conditions, in one embodiment, the displacement of a single cylinder 12 is less than or equal to 12cc. If the displacement of the cylinder 12 is too large, for example, more than 12cc, the load of the slide 14 is too large, which is disadvantageous for the thinning design of the slide 14. In this embodiment, through the optimization design of the displacement of the air cylinders 12, the displacement of the air cylinders 12 is smaller than or equal to 12cc, so that the air cylinders 12 can be matched with the sliding sheets 14 meeting the above conditions, which is beneficial to the thinning design of the sliding sheets 14, and further can effectively improve the volumetric efficiency of the compressor, reduce the abrasion, and improve the efficiency and reliability of the compressor.
On the basis of the above embodiment, in an embodiment, the compression mechanism 10 further includes a main bearing 15 and a sub-bearing 16 respectively disposed at two axial ends of the cylinder 12, the crankshaft 11 further includes a main shaft 112 for sleeving the main bearing 15, and a sub-shaft 113 for sleeving the sub-bearing 16, the cylinder 12 is provided with an exhaust notch, and the main bearing 15 and/or the sub-bearing 16 are provided with an exhaust port communicating with the exhaust notch.
In this embodiment, the main bearings 15 and the auxiliary bearings 16 are respectively disposed at two axial ends of the cylinder 12, and the main bearings 15, the auxiliary bearings 16 and the cylinder 12 cooperate to define a compression cavity, which is beneficial to the sealing reliability of the compression cavity, and the main bearings 15 and the auxiliary bearings 16 can also support the crankshaft 11 to ensure the rotation stability of the crankshaft 11. The cylinder 12 is provided with an air suction port and an air discharge notch, at least one of the main bearing 15 and the auxiliary bearing 16 is provided with an air discharge port enveloping the air discharge notch, and high-pressure air in the compression cavity can be guided to the air discharge port on the main bearing 15 and/or the auxiliary bearing 16 and discharged through the air discharge notch on the cylinder 12, so that the air discharge efficiency is improved.
The utility model also provides a rotary compressor, which comprises a shell 30, a driving motor 20 and a compression mechanism 10, wherein the driving motor 20 and the compression mechanism 10 are arranged in the shell 30, and the driving motor 20 is in driving connection with a crankshaft 11 of the compression mechanism 10. The specific structure of the compression mechanism 10 refers to the above embodiment, and since the rotary compressor adopts all the technical solutions of all the embodiments, at least the technical solutions of the embodiments have all the beneficial effects, and are not described in detail herein.
The utility model also provides a refrigeration cycle device comprising the rotary compressor. The rotary compressor comprises a shell 30, a driving motor 20 and a compression mechanism 10, wherein the driving motor 20 and the compression mechanism 10 are arranged in the shell 30, and the driving motor 20 is in driving connection with a crankshaft 11 of the compression mechanism 10. The specific structure of the compression mechanism 10 refers to the above embodiment, and since the refrigeration cycle device adopts all the technical solutions of all the embodiments, at least has all the beneficial effects brought by the technical solutions of the embodiments, and will not be described in detail herein.
The foregoing description is only of the preferred embodiments of the present utility model and is not intended to limit the scope of the utility model, and all equivalent structural changes made by the description of the present utility model and the accompanying drawings or direct/indirect application in other related technical fields are included in the scope of the utility model.
Claims (10)
1. A compression mechanism for a rotary compressor, the compression mechanism comprising:
a crankshaft including an eccentric shaft;
the cylinder is provided with a compression cavity and a sliding vane groove communicated with the compression cavity;
the piston is sleeved on the eccentric shaft and can eccentrically rotate in the compression cavity; and
the sliding vane is arranged in the sliding vane groove in a reciprocating sliding manner, and the head part of the sliding vane is propped against the outer diameter surface of the piston;
the inner diameter of the cylinder is D, the outer diameter of the piston is R, the eccentric amount of the eccentric shaft is e, the thickness of the sliding vane is T, and the head radius of the sliding vane is Rv; at least one of the following relationships is satisfied:
0.16≤T*Rv/R≤0.31；
0.17≤T*e/D≤0.29。
2. the compression mechanism of claim 1, wherein the cylinder has an inner diameter D that satisfies: d is more than or equal to 26mm and less than or equal to 44mm.
3. The compression mechanism of claim 1, wherein the height H of the cylinder satisfies: h is less than or equal to 22mm.
4. The compression mechanism of claim 1, wherein the slide has a thickness T that satisfies: t is less than or equal to 3.1mm.
5. The compression mechanism of claim 1, wherein the length L of the slide satisfies: 2e/L is less than or equal to 0.4.
6. The compression mechanism of claim 1, wherein the slider head is provided with a hard film; or the whole surface of the sliding sheet is provided with a hard film.
7. The compression mechanism of claim 1, wherein the displacement of an individual one of the cylinders is less than or equal to 12cc.
8. A compression mechanism as claimed in any one of claims 1 to 7, wherein the compression mechanism further comprises a main bearing and a sub-bearing provided at respective axial ends of the cylinder, the crankshaft further comprises a main shaft for the main bearing to socket, and a sub-shaft for the sub-bearing to socket, the cylinder is provided with an exhaust slit, and the main bearing and/or the sub-bearing are provided with an exhaust port communicating with the exhaust slit.
9. A rotary compressor comprising a compression mechanism as claimed in any one of claims 1 to 8.
10. A refrigeration cycle apparatus comprising the rotary compressor of claim 9.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202223265849.0U CN218934727U (en) | 2022-12-05 | 2022-12-05 | Compression mechanism, rotary compressor and refrigeration cycle device |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202223265849.0U CN218934727U (en) | 2022-12-05 | 2022-12-05 | Compression mechanism, rotary compressor and refrigeration cycle device |
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| Publication Number | Publication Date |
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| CN218934727U true CN218934727U (en) | 2023-04-28 |
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| CN202223265849.0U Active CN218934727U (en) | 2022-12-05 | 2022-12-05 | Compression mechanism, rotary compressor and refrigeration cycle device |
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